Coil winding machine



y 1934- E. SNYDER I 1,956,632

' con, WINDING MACHINE Filed Aug. 12, 1930 V 7 Sheets- Sheet 1 \g I INVENTOR @d fowaw/ Jxryoa A TTORNEYJ y 1934- I E. SNYDER, 1,956,632

COIL WINDING MACHINE Filed Aug. 12, 1930 (Sheets-Sheet 2 J r I 'INVENTOR v I Edward 634/042,

A TTORNEK? May 1, 1934. E. SNYDER COIL WINDING MACHINE Filed Aug. 12, 1930 '7 Sheets-Sheet 3 INVENTOR fowarofiyver B Y ((5 my I m A TTORNE YS' x QM May 1, 1934. E. SNYDER COIL WINDING MACHINE Filed Aug. 12, 1950 7 Sheets-Sheet 4 A AAAAA 0 m. WWW wm M W M May 1, 1934.

E. SNYDER 1,956,632

COIL WINDING MACHINE Filed Aug. 12, 1930 7 Sheets-Sheet 5 INVENTOR Zan/ara J/ryoer a /aofh mm A TTORNE YS May 1, 1934. SNYDER COIL WINDING MACHINE Filed Aug. 12, 1930 '7 Sheets-Sheet 6 INVENTOR Edward Jig/0?! BY I duff W ATTORNEYS May 1, 1934. E. SNYDER con, WIND'ING MACHINE Filed Aug. 12, 1950 7 SheetsSheet 7 INVENTOR Edward 625/0? BY 7.? 67,37 ATTORNEYS May 1, 1934 Patente PATENT I OFFICE rrso STATES 1,956,632 ooIL WINDING MACHINE Edward Snyder, Fort Wayne, Ind., assignor to General Cable Corporation, New York, N. Y., a corporation of New Jersey Application August 12, 1930, Serial N0. 474,723

4 Claims.

This and other objects which will be apparent to those skilled in this particular -art are accomplished by means of the invention illustrated in the accompanying drawings in which- Fig. 1 is a front elevation of the machine, a portion of one of the operating levers being cut away;

Fig. 2 is a rear elevation of the machine, a portion of the supply spool being cut away, and the winding mandrel being omitted;

Fig.3 is a plan view of the machine, a portion being broken away;

Fig. 4 is an end elevation of the machine in position to operate;

Fig. 5 is an enlarged detail elevation of meansfor adjusting the stroke of the traverse bar, parts being in section and broken away;

Fig. 6 is an enlarged front elevation of the clutch and the brake for the driving mechanism,

and also means for throwing the clutch and brakeinto and out of action;

Fig. '7 is an enlarged elevation of an epicycloidal gearing for actuating the guide and feed mechanisms;

Fig. 8 is a horizontal section projected from Fi 7;

Fig. 9 is an enlarged detail vertical section including the feed bar, the pawl and the ratchet engaged therewith, the follower and the latch shaft;

Fig. 10 is a detail plan view of the feeding mechanism, parts being in section; and

Fig. 11 is a front elevation of the lubricating device for the wire as it is fed to the mandrel.

The particular embodiment of the present invention which has been chosen for illustration is shown in connection with a machine provided with a drive shaft 1 mounted in bearings 2 positioned upon a bench 3. The drive, shaft is actuated by a motor 4 through the medium of 'a belt 5, clutch wheel 6, countershaft '7 and chain 8, the countershaft being mounted in hangers 9 suspended from the bench 3. The drive shaft 59 has on its rear end a handwheel 10 and a removable winding arbor 11 upon which areformed coils 12.

The countershaft 7 (Fig. 6) is hollow and has therein a longitudinally movable rod 13 having secured thereon a yoke 14 for operating the clutch 15 by which the'clutch pulley 6 is actuated, there being provided a spring 16 acting against the yoke, while the clutch is normally engaged with the pulley through action of the clutch spring 17.

The rod 13 extends through a bracket 18 having thereon a stationary brake plate 19, and said rod has secured thereon a brake wheel 20 adapted to have frictional engagement with the brake plate when the rod 13 is moved so as to throw the clutch out of action. The opposite end of the rod 13 has secured thereon a cam 21 that bears against a stationary cam face 22 positioned on the end of the adjacent hanger 9 so that when the cam 21 is adjustably turned, the rod 13 is moved endwise. When the rod 13 is moved toward the right hand, (Fig. 6) the clutch 15 is thrown out of action and the brake 20 is applied so that rotation of the countershaft is stopped, and when the rod 13 is moved toward the left the brake wheel is disengaged and the clutch is let into action.

The cam 21 (Fig. 4) has secured thereon a tangent arm 23 and a radial arm 24, the latter having a post 25 adjacent its outer end connected by a retracting spring 26 to the forward part of the bench. A stationary bumper 2'1 is positioned in the bench by which turning movement of the cam 21 is limited because of contact of the arm 23 with the bumper, at which time the clutch is thrown out of action and the brake 20 is applied.

A rocking latchshaft 28, provided with an operating lever 29, extends beneath the top of .the bench and has secured thereon a latch 30 that engages the arm 24, whereby the cam 21 is held so that the clutch 15 remains in action and the brake 20 out of action. By rocking the shaft 28 the latch 30 becomes disengaged from the arm 24, whereupon the cam 21 is turned through action of the spring 26, causing disengagement of the clutch and application of the brake, and operation of the machine is stopped. The latch shaft 28 has thereon an arm 31 (Figs. 2 and 4) connected by a spring 32 to one end of the bench, which tends to hold the latch 30 in engaging position.

A stub shaft 33 is mounted in a bracket 34 in axial alignment with the cam 21 and has mounted upon its end, adjacent said cam, an arm 35 having at its outer end a pin 36 that projects across the path of the radial arm 24 so as to have engagement therewith. A starting lever 37 is mounted upon a rock shaft '38 beneath the top of the bench, the lower end of which lever is connected with the swinging arm 35 by means of a pair of links 39, so that upon operation of the starting lever 3'7 the arm 35 is swung upon the axis of the stub shaft 33, whereupon, through engagement of the pin 36 with the arm 24, the cam 21 is turned into latched position. A spring 40 connecting the lever 37 and the front of the bench, holds said lever in normal position, and a bumper 37 limits the return action of said lever.

A wire tensioning mechanism is provided for maintaining a substantially constant tension on the wire being fed to the winding mandrel. Upon the bench 3 is mounted a supply spool holder, consisting of a rotatable shaft 41 mounted in bearings 42, upon one end of which shaft is removably mounted a supply spool 43 from which wire 44for making the coils is withdrawn. Upon the shaft 41 is secured a brake drum 45, and upon the adjacent bearing 42 is secured a stationary cross beam 46, to one end of which are pivoted semi-circular brake bands 47. Upon the opposite end of the cross beam 46 is pivotally supported a brake lever 48 to which are connected the corresponding ends of the brake bands 47. Upon rocking of the lever 48, the brake bands 47 are contracted about the drum 45 and rotation of the spool shaft 47 is thereby resisted. The brake lever is actuated by a rock shaft 49 which is mounted in brackets 50 on the bench, and has an arm and link connection 51 with the brake lever 48. Action of the rock shaft 49 is restrained by springs 52 that are connected respectively with the opposite ends of a lever 53 on the shaft 49.

Upon the rock shaft 49 is secured a boom 54 having at its outerend a sheave 55, the boom having vertical swinging movement to an extent limited by an overhanging bracket 56.

Upon the bench 3 adjacent the .end of the boom arm 54 is positioned a standard 57 at the upper end of which is supported a tension wheel 58, and in front of the standard is arranged a horizontal rod 59 having thereon a loose pulley 60 that turns freely and has longitudinal movement on the rod 59. The wire 44, as it is withdrawn from the spool 43, passes beneath the idler 55 on the boom 54 and over and around the tension wheel 58, and under the loose pulley 60. From thence the wire 44 extends to the mandrel 11 upon which the coil 12 is wound, and receives guidance by a pair of sheaves 61 and 62 that are supported upon a cross bar 63 loosely pivoted on the outer end of a traverse bar 64, 64'. Also, the wire 44, in passing from the sheave 61 to the sheave 62, receives lubrication from an oiling device 65 which is positioned between the sheaves and supported by the traverse bar 64.

The traverse bar 64.is slidably mounted in a support 66 in which it has longitudinal reciprocating movement, such movement being imparted through the medium of a lever 67 which is actuated by a heart cam 68 mounted upon a vertically disposed cam shaft 69. A roller 70, mounted on a sliding plate 71, extends into a slot 72 in the lever 67 and bears also against the adjacent edge of the heart cam 68, and another roller 73, mounted upon a bell crank 74 which is pivoted on the plate 71, bears against the side of the heart cam 68,]opposite to that of the roller 70. The bell crank 74 is restrained by a spring 75 so that lost motion between the heart cam, the plate 71 and the lever 67, is obviated.

The traverse bar 64 has secured thereto 2. s10 ted cross head 76- (Figs. 3 and 5) having therein a slidable block '17 provided with a roller 78 that projects into an elongated slot '79 in the lever 67. An adjusting screw 80 in the cross head is threaded in the block 77, by means of which the block is adjusted in the cross head and the le gth 9;

stroke imparted by the lever to the traverse bar is lengthened or shortened.

Driving mechanism for the cam shaft is operated from the rotary winding spindle and includes a modified form of epicyclic gearing to produce an intermittent movement of the traverse mechanism.

The cam shaft 69 is actuated through bevel gears 81, shaft 82 and gear train 83, the latter being operatively related with an internal gear 84 that is mounted in alignment with the drive shaft 1 upon a separate shaft 85 journaled in a bearing 86. As the internal gear 84 rotates, the cam shaft 69 revolves accordingly.

One end of the drive shaft 1 (Figs. 7 and 8) has a concentric extension 87 that projects into a bearing 88 centered in the internal gear 84, by which alignment of the shafts 1 and 85 is maintained. Said shaft 1 has adjacent said extension an eccentric 89 having thereon a bearing 90 which supports an epicycle gear 91 that meshes with the internal gear 84. The pitch line of the gear 91 is of less diameter than that of the internal gear 84 to an extent equal to the throw of the eccentric 89, and the point of engagement between the teeth of the gears 91 and 84 is circumgyratory and follows the pitch circle of the internal gear 84.

A standard 92 is mounted upon the bench adjacent the gear 91, through which standard the shaft 1 loosely extends, and said standard has thereon a bracket 93 provided with an arm 94, the bracket being rotatably adjustable on the standard concentrically with respect to the shaft 1. The arm 94 has pivoted thereon a link 95 which is connected with a wrist pin 96 on the gear 91, said wrist pin being locatedon said gear at a point adjacent the perimeter thereof. Thebracket 93 has a set screw 97 for securing it in adjusted positions upon the standard 92. In this manner rotation of the gear wheel 91 upon its axis is pre vented. As the shaft 1 revolves, the eccentric 89 causes vacillation of the gear 91 upon the wrist pin 96, so that said gear travels upon an orbit about the axial center of the gear 84.

The gears 91 and 84 are unequal in size, and during each cycle of movement of the gear 91, the gear 84 is progressed to the extent of the inequality of the gears. The drive shaft 1 is rotated at a constant speed, and as the gear 91 is moved about itsorbit by the eccentric 89, the tangent point of the pitch circles of the gears 91 and 84 travels entirely around the pitch circle of the gear 91 with the result that the gear 84 is progressed rotatively upon its axis to the extent of the inequality of the gears. As the gear 91 vacillates'upon the wrist pin 96, the movement imparted to the gear 84 is more pronounced at that period in the cycle when the tangent point of the gears reaches the position diametrically opposite the wrist pin, and when said tangent point reaches the position diametrically out from the wrist pin, the movement imparted to the gear 84 is negligible, as it is also during the travel of the tangent point for a considerable distance in passing the wrist pin. Thus, progression of the gear 84 is intermittent and is confined to a limited portion of each cycle of the gear 91, and the traverse bar 64 which is operatively related with the gear 84 is therefore intermittently progressed, once upon each revolution of the winding mandrel. By this means the position of the guide sheaves 61 and 62 is constant during the major portion of each revolution of the winding mandrel 11, so that the Wire 44 is wound upon the mandrel during said major portion in a plane at right angles to the axis of the mandrel, and during the remainder of each revolution the position of said guide sheaves is advanced so that the wire 44 will sidelap the previous turn when the next turn is being wound. By adjustment of the bracket 93 on the standard 92, the advancing movements of the traverse bar may be timed with respect to the mandrel so that said advancing. movements will occur at any desired predetermined point in the revolutions of the mandrel. In this manner the sidelaps of the wire 44, as the turns are wound upon the mandrel, are uniformly located thereon.

The machine is provided with automatically operated mechanism for stopping the machine at the conclusion of the winding operation, or when the coil formed on the mandrel has been completed. This mechanism is operatively related with the winding mandrel and the traverse bar through the medium of the gear train 83, heart cam 68 and associated parts. The stop mechanism consists of a feeding device (Figs. 1, 9 and 10) composed of a spring restrained reciprocating bar 98- actuated by an eccentric 99 mounted on the lower end of the cam shaft 69, there being a roller 100 on the end of the bar 98 that bears against the rim of the eccentric. As the cam shaft 69 revolves, the bar 98 is actuated. A spring restrained feed bar 101 is mounted in parallel relation with said reciprocating bar and has two series of saw teeth 102 and 103 and a longitudinal slot 104 extending vertically through the bar between the two series of teeth. The reciprocating bar 98 has pivoted thereon a ratchet 105 provided with a laterally extending lug 106, the ratchet having engagement with the teeth 103 on the feed bar. A rock shaft 107, supported in connection with the bench, has on its forward end a pawl 108 that has engagement with the series of teeth 102 on the feed bar, and underlies the lug 106 on the ratchet, so that when the pawl is raised by turning the rock shaft 107, the ratchet is also raised thereby, whereupon the feed bar automatically moves to its starting point against a bumper 109. The rock shaft 107 has an arm 110 secured thereon having a rigid projection 111 that is connected by a spring 112 to the top of the bench, whereby the rock shaft is nomally held so that the pawl 108 .engages the corresponding teeth of the feed bar, which prevents retraction thereof- Also, the arm 110 has a roller 113 pivoted thereon that bears against a cam 114 secured on the rock shaft 38 which is actuated by the starting lever 37, whereby the pawl 108 and the ratchet 105 becomes disengaged from the feed bar upon operation of the starting lever.

The rock shaft .107 has also secured thereon a pendant arm 115 that extends into the path of another arm 116 which is secured; on the latch shaft 28, whereby said pawl andratchet may be thrown out of engagement with the feed bar upon manipulation of the latch lever 29. Another arm 117 secured on the latch shaft 28 extends up through the slot 104 in the feed bar 101, and is engageable by a pin 118 that is adjustably positioned transversely in the feed bar, so that as the feed bar is progressed through action of the ratchet 105, the latch shaft 28 is turned through engagement of the arm 11'! by the pin 118, thus causing disengagement of the latch 30 from the arm 24 on the cam 21, whereupon, the clutch 15 is thrown: out and the brake 20 is applied The arm 115 on the rock shaft 107, and the arm 116 on the latch shaft 28, are so positioned upon their respective shafts-that their engagement may take place only after the latch shaft 28 has been moved farther than is necessary to release the latch 30 from the arm 24 on the cam 21. Under normal conditions operation of the machine is stopped upon release of the latch 30 from engagement with the arm 24 withoutthe pawl and ratchet becoming disengaged from the feed bar. However, when the latch shaft 28 is turned beyond the point of releasing the latch from the arm 24, the rock shaft 107 is turned through engagement of the arms 115 and 116, causing the pawl and ratchet to be raised, and consequently resetting of the feed bar 101 against the bumper 109 thereupon takes place.

I have found that the proper relative positioning of the individual turns of wire is materially assisted if the wire is provided with a coating of lubricant or the like prior to winding it into coil form. As illustrated, this is accomplished by means of a drip cup 65' supported upon a bracket 64 on the end of the traverse bar 64', and a pair of wicks 119 secured upon a spike 120 beneath the outlet of the drip cup, the lower end of one wick extending into a catch pan 121 supported by the bracket 64". The wire 44, in passing from the sheave 61 to the sheave 62 is drawn between the wicks and becomes moistened by the lubricant received from the drip cup and with which the wicks are saturated.

The tilting cross bar 63, upon which the sheaves 61-62 are supported, is yieldingly sustained in normal position by a spring 122 secured in the traverse bar 64', the ends of which spring bear upwardly against the corresponding pin 123 that project from the cross bar 63.

In operating the machine, the bumper 109 is so adjusted and the pin 118 is so positioned in the feed bar 101 as may be required to insure the desired duration of the operation of the machine from the starting point until the predetermined number of turns and layers of the wire 44 shall have been wound upon the mandrel, at which time the machine is automatically stopped through action of the pin 118 against the arm 11'! on the latch shaft 28 (Figs. 1 and 9).

Before attaching the wire 44 to the mandrel, the machine is thrown into action by operating the starting lever 37, and is allowed to run idly until the guide sheaves reach the position in front of one end or the other of the mandrel as may be required for starting the winding operation. The machine is stopped by operating the latch lever 29. Also, the mandrel may be turned preoisely to the desired point in its cycle by manipulating the hand-whee1. 10. The wire .44 is then attached to the mandrel in the usual manner in readiness for the winding operation. The starting lever 37 is then operated which causes the release of the pawl and ratchet from the feed bar and permits said feed bar to assume its starting position against the bumper 109, and also, causes the brake 20 to release and the clutch to be thrown into action and consequent operation of the machine.

The outer end portion 64' of the traverse bar is longitudinally adjustable in its other portion 64, which permits alignment of the guide sheaves with respect tothe heads of the mandrel, and by turning the screw the stroke of the traverse bar is adjusted to conform with the length of the coil to be wound.

Although I have described one embodiment of this invention in considerable detail, it will be apparent that various changes, additions, omissions and substitutions can bemade therein without departing from the spirit of this invention or the scope of the appended claims.

What I claim as new and desire to secure by Letters Patent is:

1. The combination in a coil winding machine of a winding mandrel, a traverse mechanism, a power shaft for operating said mandrel and said mechanism, a clutch for controlling the operation of said shaft, a brake associated with said shaft, means connecting said clutch and brake for simultaneous operation thereof, a latch for permitti'ng engagement of said clutch and preventing operation of said brake, means for manually setting said latch and means operated by rotation of said shaft for releasing said latch to disengage said clutch and apply said brake.

2. The combination in a coil winding machine of a rotary winding mandrel, a traverse mechanism, a drive shaft for operating said mandrel and said mechanism, a clutch for controlling the operation of said shaft, a brake associated with said shaft, means operable by said machine for disengaging said clutch and operating said brake at a predetermined point in the operation of said machine, a starting lever for releasing said brake and permitting engagement of said clutch, a controlling latch for maintaining said clutch in engagement and a lever for releasing said latch to disengage said clutch and operate said brake.

3. The combination in a coil winding machine of a winding mandrel, a traverse mechanism for guiding the wire delivered to said mandrel, a power shaft for operating said. mandrel and said mechanism, a clutch for controlling the operation of said shaft, a 'brake associated with said shaft, means for simultaneously controlling said clutch and brake, a feed bar, means operated by said machine for moving said feed bar, means on said feed bar for operating said clutch and brake at a predetermined point in the operation of said traverse mechanism, means for manually operating said clutch and brake at any point in the operation of said machine and means operated thereby for selectively resetting said feed bar.

4. The combination in a coil winding machine of a winding mandrel, a traverse mechanism for feed bar for operating said clutch and brake at a predetermined point in the operation of said traverse mechanism, means including a latch shaft for holding said clutch in engagement and said brake released, means for moving said latch shaft to release said clutch and engage said brake and means operated by further movement of. said latch shaft ror resetting said feed bar.

EDWARD SNYDER. 

